CA2026185A1 - Ceramic bearing - Google Patents
Ceramic bearingInfo
- Publication number
- CA2026185A1 CA2026185A1 CA002026185A CA2026185A CA2026185A1 CA 2026185 A1 CA2026185 A1 CA 2026185A1 CA 002026185 A CA002026185 A CA 002026185A CA 2026185 A CA2026185 A CA 2026185A CA 2026185 A1 CA2026185 A1 CA 2026185A1
- Authority
- CA
- Canada
- Prior art keywords
- ring
- ceramic
- outer ring
- inner ring
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/043—Sliding surface consisting mainly of ceramics, cermets or hard carbon, e.g. diamond like carbon [DLC]
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Ceramic Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Abstract of the Disclosure The ceramic product of this invention is characterized in that the ceramic bearing constructed by being allowed to contact the ceramic outer ring slidably with the ceramic inner ring is provided with a latching member to prevent the transfer of the ceramic inner ring in the axial direction at the inner or the outer ring of said ceramic product.
The bearing constructed by the sliding contact of -the ceramic inner ring with the ceramic outer ring can prevent the occurrence of the transfer of the inner ring in the axial direction with respect to the outer ring by providing a latching member which prevent the -transfer of the inner ring in the axial direction at the inner or outer ring. Accordingly, there is no anxiety of separation of the outer ring from the inner ring.
The bearing constructed by the sliding contact of -the ceramic inner ring with the ceramic outer ring can prevent the occurrence of the transfer of the inner ring in the axial direction with respect to the outer ring by providing a latching member which prevent the -transfer of the inner ring in the axial direction at the inner or outer ring. Accordingly, there is no anxiety of separation of the outer ring from the inner ring.
Description
20261~
Speclflc~tion Title of the Inventioll ;
Ceramic Bearing Field of the Invention ;
This invention relates -to a ceramic bearing constructed by combining a ceramic inner ring and a ceramic outer ring, particularly to a ceramic bearing whereln -the ceramics inner ring prevents movement of the ceramics outer rlng ln an axlal direction.
Description oP the Prior Art ;
It is generally performed to use a sliding bearing or a rolling bearing in a case of attaching an axis of rotation to a machine frame.
~ s a rolling bearing, such kinds of a ball bearing, a roller bearing and a needle bearing havlng a rotary member such as balls, rollers and needles is situated between -the inner ring and the outer ring. Further, there exist bearings such as radial bearings, thrust bearing and like according to a supporting system of a load which act~ on an axis engaged with the inner ring. ~ deep-groove type bearing, an angular type bearing, and a -taper roller bearing and etc. are known as the bearing enabling to support the shaft to which a radial load and a thrust load are simultaneously applied. These many rolling bearings are standardized. Accordingly, on deslgning a machine, the most suitable one is selected and employed.
Speclflc~tion Title of the Inventioll ;
Ceramic Bearing Field of the Invention ;
This invention relates -to a ceramic bearing constructed by combining a ceramic inner ring and a ceramic outer ring, particularly to a ceramic bearing whereln -the ceramics inner ring prevents movement of the ceramics outer rlng ln an axlal direction.
Description oP the Prior Art ;
It is generally performed to use a sliding bearing or a rolling bearing in a case of attaching an axis of rotation to a machine frame.
~ s a rolling bearing, such kinds of a ball bearing, a roller bearing and a needle bearing havlng a rotary member such as balls, rollers and needles is situated between -the inner ring and the outer ring. Further, there exist bearings such as radial bearings, thrust bearing and like according to a supporting system of a load which act~ on an axis engaged with the inner ring. ~ deep-groove type bearing, an angular type bearing, and a -taper roller bearing and etc. are known as the bearing enabling to support the shaft to which a radial load and a thrust load are simultaneously applied. These many rolling bearings are standardized. Accordingly, on deslgning a machine, the most suitable one is selected and employed.
2~2~8~
~ e above ~ ling bearltlys are made or constructed of a metal supporter macle of s-teel, cast iron, copper and the llke laminated a white metal layer -thereon or laminated an oil including a:lloy or embed it thereorl. Further, some sliding bearings are made or constructed by gun metal, synthetic resin and the like formed to a sleeve shape.
Generally, in conventional sliding bearings, a bearing which supports a radial load and a beariny which supports a thrust load are separately standardized.
The above rolling bearing and the sllding bearing have peculiar charac-teristics respectively. Accordingly, in employment the most suitable one is used considering these characteristics.
However, even the above rolling bearings and the sliding bearings have troubles.
Namely, in the rolling bearing flaking phenomenon due to rolling fatigues is happened which determines its life necessarily. By this, because the thermal resistance is low and the number of constructing parts thereof increases, the cost oP
the produc-t becomes high. Further, in the above sliding bearing the friction loss increases due to the sliding contact of the outer periphery o~ the axis with the inner periphery, By -this, there occurs ~uch problem as necessity of applying a reinforced lubrication or a self lubrication to the contact surface of the axis with the bearing.
On the other hand, ceramics having high compressive strength, friction resistance and small friction coefficient, 2 ~ 8 5 have been developed recently.
Further, a prior art disclosed ln USP Mo.~,63~,300 relates to a rolling bearillg constructed by uSilly a ceramic roller as a rolling body. Accordirlg to thi~ technique, lt is possible to constitute a rolling bearing havil-g a heat resistance and an anti-corrosion, but :number of parts products which constitute the bearing increases.
In order -to solve the above problems,the applicant o~
this lnvention has developed many kinds of ceramic bearings and submitted patent applications (Japanese Patent ~pplication No.63-325933 etc.).
Summary of the Invention ;
The main object of this invention is to provide a ceramic bearing to solve the above problems, particularly a ceramic bearing constructed by the sliding contact o~ the inner ring of ceramic product with the outer ring of ceramic product, said ceramic bearing being able to prevent to move the inne~ ring of the ceramic product in an axial direction with respect to the outer ring of the ceramic product.
Another ob~ect of this invention i5 to provide a bearing having small numbers of parts by constructing the inner and outer rings by means of ceramics.
Accordingly, in order to a-t-tain these objects the ceramic product of this invention is characterized in that the ceramic bearing constructed by being allowed to contact the ceramic outer ring slidably with the ceramic inner ring is provided with 2026~
a latcllirlg member to prev~ t the transfer o~ the ceramic inner ring in the axial direction at the inner or the outer ring of sald ceramic product.
~ s descri~)ed .in this invention, the bear;ing constructed by the sliding contac-t of the ceramic inner rlng (hereafter referre~ to as "inner ring") with the ceramic outer ring (hereafter referred to as "outer ring") can prevent the occurrence of the transfer of the inner rlng in the axial direction with respect to the outer rlng by providing a latching member which prevents the transfer of the inner ring in the axial direction at the inner or outer ring. ~ccordingly, there is no anxiety of separation of the outer ring from the inner riny.
Further, since the bearing i5 constructed by outer and inner rings, number of parts decreases as compared wlth the conventional rolling bearing, thereby being able to decrease its cost.
Since the axis is engaged with an axial hole formed at the inner ring, the slidlng does not happen between the axis and the inneS ring. Accordin~ly, there i5 no anxiety of the occurrence of the wear at the axis even after long period of use.
Furthermore, a sliding friction is very low due to the construction made of the inner and outer ceramic rings. By thi~, the thermal generation due to the friction can be lowered.
Slnce the expansion due to the heat is low, the occurrence of stress to a machine frame or the axis is possible to be lower.
202G'l~
~rlef t:le~cl:lpi:io~l o~ th~ llrawi~lg~ ;
Fig.1 is an assembl:Lng explanatory view ol the bearing in a Plrst embodimellt of thls inventioll.
Fly.2 ~s a sectional explanatory view along the line II- II
of Fig.1.
Fig.3 is an explanatory view of a guide pin in the first embodiment.
Fig.4 is an assembling explanatory v:le~v ill a second embodiment of this invelltion.
Fig.5 i5 an assembling explanatory view in a third embodlmerl t o~ thi s i nvention.
Fig.6 is an assembling e~planatory view in a fourth embodiment of this invention.
Detailed description of the Preferred Embodiment ;
[Example 1]
In Fig.1 to Fig.3, the bearing A comprises an inner ring 1 to be engaged with the axis, an outer ring 2 to be attached to a machine frame or a casing and a plurality of gu:lde pins 3 fi-t to the outer ring 2.
The inner ring 1 is formed by press~formlng an oxide ceramics material of a material such as PSZ (partially stabilized Zirconia) or alumina, etc. by filling it in a mold and then sintering a molded product at 1500C to 1600CC. An axial hole 4 for engaging the axis is formed at the center of the inner ring 1. The axial hole is formed so a~ to have a fixed engaging allowance according to a diameter of the axis to be engaged with the axial hole 4.
2026'1~
I'he numeral 6 is all axial cetlter of the axial hole and corresponds to the a~ial cen-ter of the bearlng ~.
~ ~lldiny surface la i5 formed on -the outer periphery of the inner ring 1 in parallel to the axial center 5. The sliding surface la transmits a radial load applied on the axis to the outer ring 2 by the sliding contact with the sliding surfacs 2a formed at the outer ring 2 described hereinaft~r. For this purpose, the sliding surface la i5 necessary to be parallel to the axial center 5 correctly.
ht -the approximately middle portion oE the sliding surfa~e la formed on the outer periphery of the lnner ring 1, a ring shape groove b is formed all around -the inner ring 1. The groove 6 constrains the moving direction of the lnner ring 1 only in a rotational direction by latching with guide pin 3.
~ he outer ring 2 i9 also formed by press-forming filling an oxide ceramics material such as PSZ or alumina etc. in a mold as same as in tlle illner ring 1 and then sinterillg it at 1500 C
to 1600 C.
At the inner of the outer ring 2, a sliding surface 2a formed so as to have a fixed allowallce with respect to the sliding surface la formed on the outer periphery of the inner ring 1 is formed. The sliding surface 2a is formed so as to have an approximately equivalent length to the sliding ~urface la of the inner ring and contacts with the sliding surface la slidably whereby a radial load applied on the axis is transmitted through the inner ring 1. For this purpose, the sliding surface 2a is construc-ted by a parallel surface to the ~2~18~
axial centet~ 5.
~ p].urality of holes 7 for erl~clylt~g g-licle pins 3 are formed at approximately midclle portion in the axial direc-tion of the outer riny 2 and positions corresportcl:itlg to the groove 6 formed a~ the inner ring 1. The sllape of the hole 7 is that of the guide pin 3, namely a circular sha]?e or a polygon ancl the dimension thereof is formed to be approxlmately equivalent to that of the gulde pin 3.
The outer periphery 2b of the outer ring 2 ls formed to be cylindrical sllap~ parallel to the axi~l center 5. The both end surfaces ~c of tlle o~-ter ring 2 i5 con~trllcted as a rectangular plane against the axial center 5. The outer periphery 2b arld the end surface 2c become engaged por-tions when they are a-ttached to a machine frame or a Ca.SinCJ not illustrats the b.earing A.
The guide pin 3 i5 formed by press-forming an oxide ceramics material sucll as PSZ and alumina etc. filling it in a mold and sintering a molded produc-t thereof at approximately 1500~C to 1600 C.
The guide pin 3 may be so called a straight pin or a taper pin. Further, a shape of guide pin 3 (3a to 3c) may be a cylindrical pin 3a as ~hown in Fig,3(A) or may be a square pin 3b as SIIOWII itl Fig.3(B). Further, a pin 3c having a flange at the end portion as shown in Fig.3(C) may be usecl. In -this embodiment, the cylindrical pin 3a is used as guide pin 3.
The guide pin 3 i5 formed to be equal to -the wide dimension of the groove to formed at the inner ring 1 or to _ ~ _ 202~.85 some~ al- small dlm~ ion thereof. ~ccordlllgly, th~re i~ no an~ciety of occurrence o~ play hetween the gu:lcle pin3 and groove 6.
Further, number of guide pin 3 i5 desirable -to be 3 or more than 3. This is due tc the fact when number of guide pin is few and a load in a thrust direction applies on the axls of the inner ring 1, there i5 anxiety that a bellding stress applie~
to the guide pin 3 due to said load.
I'he axial hole 4, the sliding surface la, tlle groove 4 in the inner ring 1 and the sliding surface 2a, the outer periphery 2b, the end surface 2a and the hole 7 etc. in the outer xlng 2a are formed simultaneously when the inner and outer rings are press-formed.
In t~le above press forming, the dimensiorl accuracies of the inner ring 1 and the outer r-ing 2 are possible to obtain approximately~ 0.005mm in accuracy against designed dimension of each part. Further, surface roughness can be secured about R~ O.B.
In order to construct the bearing A using the inner ring 1, outer ring 2 and guide pin 3 constructed as shown in the above, the sliding surface 2a i5 allowed -to contact wit~ the sliding surface la slidably by engaglng the inner ring 1 with the outer ring 2. The groove 6 formed at the inner ring 1 is opposed to the hole 7 formed at the outer ring 2 and the guide pin 3 is inserted in-to each hole 7, top end of said guide pin 3 being allowed to latch with groove 6.
~t this time, the guide pin 3 can be adapted to fix to 202618~
t}le oute~ rilly 2 by applyillg an adlle3ive to tlle~ corresponding part ~Jit~ t}le hole 7 of thc! gu:L~e pin 3 ancl engaying said pin 3 witll llole ~. E'urtll~r, -tlle guide pill 3 can be adapted to fix to the outer ring 2 by exparlding the llole 7 hea-t:lrlg -the outer ring 2 and ellgagillg the guide pin 3 in normal temperature sta-te to the llole 7, so called thermal :insert. Furl.hermc)re, the gulde pin 3 can be adapted -to fix to the outer riny 2 by cooling the guide pin 3 to shrink by means of col~ agent such a'3 liqulde nitrogen etc. and engayillg saicl pin 3 -to the outer rillg 2 in normal state, so called coollng insert.
It is de~sirable to perform a grinding proces3ing to the sliding surface la, the groove ~ of -the inner ring 1, and the sliding surface 2a and the pin 3 of t~le outer ring 2 separately which cons-titutes the bearing A accvrdirlg to the accuracy requested for said bearing A.
Further, the lapping of the contact surface of the sliding surface 2a with the sliding surface ta, the yuide pin 3 and the groove 6 are also possible after engaging the inner ring 1 -to the outer ring 2. The lapping can be practi~ed by giving an abrasive agent such as diamond powders, etc. to each contact surface and a relative rotation tllereto.
The rotation of the bearing A becomes to be smootll by grinding the inner and outer rings and guide pin 3 and groove 6 respec-tively or lapping them.
In the bearing A constructed as described above, the top end portion of the guide pin 3 fixed to the outer ring 2 is inserted into the groove G formed at the inner ring 1. By this, g 202~18~
tlle outer ring 2 by applyin~ an adhesive to the corresponding part ~ith -t}le hole 7 of the gu:ide pin 3 and engaging said pin 3 witll ho1e 7. Further, the guide pin 3 can be adapted to fix -to the outer ring 2 by exparldiny the hole 7 heat:ing the outer ring 2 and engagillg the guide pin 3 in normal tempera-ture state to the holc ~, so called thermal insert. Furl:hermc)re, -the guide pin 3 can be adapted to fix to tlle outer ring 2 by cooling the guide pin 3 -to shrillk by means of cold agent StlCh as liquide nitroyen etc. and engagillg said pin 3 to the outer ring 2 in normal sta-te, so called cooling insert.
T t is desirable to perform a grinding processing to the sliding surface la, the groove 6 of the inner rlng 1, and the sliding surface 2a and the pin 3 of the outer ring 2 separately which cons-titutes the bearing A accvrdiny to the accuracy requested for said bearing A.
Further, the lapping of the contact surface of the sliding surface 2a with the sliding surface la, the yuide pin 3 and the groove 6 are also possible after engaging the lnner ring .t -to the outer ring 2. The lapping can be practised by giving an abra~i-ve agen-t such as diamond powders, etc. to each con-tact surface and a rel~tive rotation theretor The rotation o~ the beariny ~ becomes to be smooth by grinding the inner and outer rings and guide pin 3 and groove 6 respectively or lapping them.
In the bearing A constructed as described above, the top end po.rtion of the guide pin 3 fixed to the outer ring 2 is inserted into the groove 6 formed at the inner ring 1. By thi~, g 2(~26~l8~i 12a corre~polld~ to t~le slldiny ~ t~ ce lla 13 ~orme-l and a plane 12c which is appro~lmately r:lyllt angle W:ltll the axial aenter 15 i9 formed connecting wi~ the sllditly surfaoe 12a. ~-t a ridged line formed by the sl.idincJ surface 12a and tlle plane 12c, a very small ~aper surface formed at a taper angle equivalent to the -taper surface llb O:e the inner ring 11 is constructed, said taper surface being constrllcted as the slidillg member 12b. The slidin~ portion 12b contacts slidably with -the taper surface llb formed at the intler ritly 11 and suppo;tts a load in -the thrust direction applied on the axis engacJed wi-th tle inrler rin(3 11.
Further, the end surface 12d at the fron-t elld side of the outer riny 12 is const:ructed as a rig}lt angle surface with the axial center 15.
A-t the latchiny member 13, is formed a hole 13 at the center having a laryer diameter thatl that of the axial hole 14 formed at the inner ring 11. Further, the outer diameter of the latching member 13 is formed to be larger than that of the sliding surface lla of the inner riny 11 and smaller than that of the outer diameter of the ou-ter ring 12. Furthermore, at one surface of the latching member 13, is formed a ring shape projection 13b engaged with the groove 16 formed at the inner ring 11.
In order to construct the bearing B by the inner ring 11, the outer ring 12 and the latching member 13 constructed as above, the inner ring 11 is engaged wi-th the outer ring 12 to allow to contact tlle sliding surfaces 12a, lla and the taper -surface llb with -the sliding portion 12b slidably, and then the 2~2~18~
oJecl::loll 13b o~ tlle l.al clllng member 13 i:3 allowed to enyage w:Lth the groove 16 formed at the :Inner r:lng 11. ~fter that, the latching member 13 i3 fixed to -the i/lner rillg 11 by mean3 of applying all adhesive agent, thermal insertlon, or cooling insertioll to the projection 13b.
In -the bearing B thus constructed as described above, the sliding surface lla formed at the inner ring contacts ~lidably with the sliding surPace 12a formed at the outer ring 12 thereby being able to suppor-t the load in the radial directioll applied to the axis enyayed with the inrler ring 11, Further, the taper surface 11b formed at the inner ring 11 contacts slidably with the slidiny portion 12b formed at the outer ring 12 thereby being able to support the load in the thrust direction applied to the axis.
Thus in the bearirlg B, the taper surface llb of the inner ring 11 contacts slidably witll the sliding portion 12b of the outer ring 12 thereby preventing the transference of the inner ring 11 in a direction shown by the arrow, Since the latching member 13 fixed to the end surface llc of the ~nner ring 11 has a larger diameter than that of the sliding surface 11a, the transference of the inner ring 11 in b direction showll by the arrow can be prevented.
In Fig.5, the bearing C is constructed by the inner ring 21, the outer ring 22 and the latching member 23. The inner ring 21, the outer ring 22 and the latching member 23 are formed by forming the ceramic3 ma-terial and sintering as same as in each embodiment described above.
~02618~
Al ~ e cent~r of l:lle inller r:ing 2l, tlle a~sial hole 24 for engag~ the axls rlot il:Lustrate(l is formecl correspondirlg to the axia]. cellter 25 of the bear:Lng C.
'l'he outer ~haE)e of the :inller ring 21 is lormed to be a curved surface shape, said curved sur~ace heing constructed as a sliding surface 21a, ~-t the front side of tlle lnller riny 21 a cylindrical bos~ portion 2lb is formecl connectillg with the sliding sur~ace 21a, at the end sur~ace 21c of said boss portion 2lb being formed a ring shape groove 26 so tllat the center thereof may be corresporlded to the axlal cer-ter 25.
The inner peripllery of the outer riny 22 is formed with a shape corresponds to the shape of the sliding sur~ace 21a formed at the inller ring 21, said inner periphery .sur~ace being constructed as a sliding surface 22a. F'urther, a hole 22b is formed continuillg Witil the sliding surface 22a. The hole 22b ls formed so as to have a comparstively larger dimension than that of the outer dlameter of tlle boss port iOII 2lb ~:ormed at the inner r:ing 21.
The latching member 23 is rormed with appro7~imately same shape with said latching member 13. Namely, at the latching member 23, a hole 32a i~ provided with a larger dimension than that of a diameter of the axial hole 24 formed at the inner ring 21 corresponding to the a~.ial center 25 o~ the bearing C.
Further,formed is a projection 23b having a center corresponds to t}le ax:ial cerrter 25.
In order to constitute the bearing C by -the inner ring 21, outer ring 22 and latching member 23 constructed as 2~2~
de.scribed above tlle J.nller rilly 21 :i~ enyacJed w.Lth the outer rirlg 22 -the slicllng sur~ce 21a :i5 allowed to contact slidably wlth the sliding surface 22a and tllen the E~rojection 23b of the la-tchiny member 23 is allowed to enyage ~ith groove Z6 formed at the end surface 21c of the inllel r.ing 21. The latching member 23 is Lixe~ to -the inner ring 21 by mean~ of apply:ing an adhesive agent to the proje~tion 23 or thermal or cooliny inser-tion etc.
In the bearing C thus constructed even when the load in radial directioll and tll~ load in ~llrust direction applied simultaneously to the axis erlyaged with inner ring 21 by the sliding contact o~ the sliding surface 21a ~vith tlle sliding surface 22a said axis can be supported smoothly. Since the sliding surfaces 21a and 22a of the bearing C are formed to be a curved surface shape the bearing C possesses an automatic adjustment function.
The bearing C is possible to prevent the trnsfer of the inner ring 21 in c direction shown by tlle arrow by the contact of sliding surfaces 21a 22a and further to prevent its trnsfer in d direction sho~n by tlle arrow.
In Fiy. 6, the axis D is constructed by a cap-like latching member 33. Said inner ring 31 tlle outer ring 32 and the latching member 33 are formed by forming ceramics material and sintering it as same as in each embodiment described above.
At the center of the inner ring 31 an axial hole 34 for engaging an axis not illustrated therein is formed corresponding to the axial center 35 of the bearillg D. At the vuter periphery 202~
o~ tlle ~ ler rilly 31, a .sLldlllg suL~face 31a pclrallel 1:o the a~ial cerlter 35 i5 fOr~ne(l, 9aid sl:idlll(J surface 31a forming a -taper surface 31 conllectillcJ therewith at -the frollt slde of the inrler r:LIlg 31. Further, the cyl:illdrical sur~ace 31c is formed continuillg with said taper surface 31b.
~ t tlle inner periphe:ry of the outer riny 32, is formed the sliding surface 32a which contacts slidably with the sliding suriace 31a formed at the lnrler xlrlg 3l. ~t the ~ron~ side of the sliding surface 32a, the surface 32c approximately rectangular to the axial cerlter 35 and a cyl:lndrical surface 32d havillg a smaller diamete~ thall l:llat oL the slidlng surface 32a parallel to the axial center 35 are formed. The surface 32cl is formed with a compactively larger dimension than that of the outer diameter of the cylindrical surface 31c formecl at the inller ring 31. ~o the ridged lille constructed by the surfaces 32c and 32d is provided a sliding portion 3Zb which supports the load in -tlle thrust direction applied to the inner ring by abutting the taper surface 31b formed at -the inner riny 31 as same as in the secolld embodiment.
At the surface 32e of the rear side of the outer ring 32, a step por-tion 36a continued to the outer periphery 32f of the outer ring 32 is formed. The step portion 36a is formed to be a ring shape corresponds to the axial center 35 as its center.
The latching member 33 is formed so that the outer diameter may be approximately equivalent to the outer diameter of the outer ring 32 or a somewhat smaller diameter, and a ring shape project ion 33b havillg a cen-ter eorrespondillg to the axial 20261~
cellterl 35 is formed. 'rhe heigllt o~ the projection 33b is formed so as to ~e appro}cimately equ:lvalent -to the dep-th of the s-tep 36a. FUI~ ther, the numeral 33a is a hole formed to be a larger diameter than that of the axial hole 3~.
In order to cons-truct the bearing D by the inner and outer rings 31 and 32 respectively and the latching member 33, after engagillg tlle inner riny with tlle outer ring 32, the latching member 33 is fi~ced to the outer ring 32 by applying the adhesive ayent to the outer ring 32 or thermal insertion or cooling insertloll of -the outer ring 32 as same as ln the embodiment describe above.
In the above bearlng D, slnce -the outer per.iphery of the latching member 33 does not projec-t more than outer ring 32, an attaching working of the bearing D to the machine frame, etc.
can be performed smoothly using the outer periphery 32f of the outer ring 32 as a guide. Further, by sliding contact of the sliding surface 31a witll the sliding surface 32a, the load in the radial direction applied to the axis engaged with the lnner ring 31 is supported and by the sliding contact of the taper surface 31b with the slidiny port.ion 32b, the load in the thrust direction can be supported.
The above bearing D prevellts the transfer of the inner ring 31 in e direction shown by the arrow by the abutmen-t of the taper surface 31b against the sliding portlon 32b and prevents the transfer of the inner ring 31 in f direction shown by the arrow by the latching member fixed -to the outer ring 32.
As described above, by forminy a step portion 36a having 202~18~
a same funct.Lo~l a~ tlle ~3roove lll eacll above embodimerlt at the conrlect~ y portion of the outel peril)hery 32f allc1 the rear end e.llrface 32e of the outer r-lng 32 the form of the outer ring 32 become easy.
In each above bearing ~ to ~ since the inrler and outer rings are made by ceramics respec-tively tlle fric-tion coefficient becomes smal] thereby decreasing the frlction loss thereof. By this there is no need of tlle lubrication agains-t the sliding surface. Further even when the heat is generated due to tlle sllding there occurs no exc:eQ.s of the -thermal stre~s due to tlle thermal exparlsion of the iIIner and outer ring~
because tlle coefficietlt o~ the thermal expansion is about 8 to 11XlO 6/~C. Further since the heat temperature resistance of the ceramics is about 600'G to lOOO~C there is no fear of deterioration of the inner arld outer rings due to the heat yenerat ion .
~ e above ~ ling bearltlys are made or constructed of a metal supporter macle of s-teel, cast iron, copper and the llke laminated a white metal layer -thereon or laminated an oil including a:lloy or embed it thereorl. Further, some sliding bearings are made or constructed by gun metal, synthetic resin and the like formed to a sleeve shape.
Generally, in conventional sliding bearings, a bearing which supports a radial load and a beariny which supports a thrust load are separately standardized.
The above rolling bearing and the sllding bearing have peculiar charac-teristics respectively. Accordingly, in employment the most suitable one is used considering these characteristics.
However, even the above rolling bearings and the sliding bearings have troubles.
Namely, in the rolling bearing flaking phenomenon due to rolling fatigues is happened which determines its life necessarily. By this, because the thermal resistance is low and the number of constructing parts thereof increases, the cost oP
the produc-t becomes high. Further, in the above sliding bearing the friction loss increases due to the sliding contact of the outer periphery o~ the axis with the inner periphery, By -this, there occurs ~uch problem as necessity of applying a reinforced lubrication or a self lubrication to the contact surface of the axis with the bearing.
On the other hand, ceramics having high compressive strength, friction resistance and small friction coefficient, 2 ~ 8 5 have been developed recently.
Further, a prior art disclosed ln USP Mo.~,63~,300 relates to a rolling bearillg constructed by uSilly a ceramic roller as a rolling body. Accordirlg to thi~ technique, lt is possible to constitute a rolling bearing havil-g a heat resistance and an anti-corrosion, but :number of parts products which constitute the bearing increases.
In order -to solve the above problems,the applicant o~
this lnvention has developed many kinds of ceramic bearings and submitted patent applications (Japanese Patent ~pplication No.63-325933 etc.).
Summary of the Invention ;
The main object of this invention is to provide a ceramic bearing to solve the above problems, particularly a ceramic bearing constructed by the sliding contact o~ the inner ring of ceramic product with the outer ring of ceramic product, said ceramic bearing being able to prevent to move the inne~ ring of the ceramic product in an axial direction with respect to the outer ring of the ceramic product.
Another ob~ect of this invention i5 to provide a bearing having small numbers of parts by constructing the inner and outer rings by means of ceramics.
Accordingly, in order to a-t-tain these objects the ceramic product of this invention is characterized in that the ceramic bearing constructed by being allowed to contact the ceramic outer ring slidably with the ceramic inner ring is provided with 2026~
a latcllirlg member to prev~ t the transfer o~ the ceramic inner ring in the axial direction at the inner or the outer ring of sald ceramic product.
~ s descri~)ed .in this invention, the bear;ing constructed by the sliding contac-t of the ceramic inner rlng (hereafter referre~ to as "inner ring") with the ceramic outer ring (hereafter referred to as "outer ring") can prevent the occurrence of the transfer of the inner rlng in the axial direction with respect to the outer rlng by providing a latching member which prevents the transfer of the inner ring in the axial direction at the inner or outer ring. ~ccordingly, there is no anxiety of separation of the outer ring from the inner riny.
Further, since the bearing i5 constructed by outer and inner rings, number of parts decreases as compared wlth the conventional rolling bearing, thereby being able to decrease its cost.
Since the axis is engaged with an axial hole formed at the inner ring, the slidlng does not happen between the axis and the inneS ring. Accordin~ly, there i5 no anxiety of the occurrence of the wear at the axis even after long period of use.
Furthermore, a sliding friction is very low due to the construction made of the inner and outer ceramic rings. By thi~, the thermal generation due to the friction can be lowered.
Slnce the expansion due to the heat is low, the occurrence of stress to a machine frame or the axis is possible to be lower.
202G'l~
~rlef t:le~cl:lpi:io~l o~ th~ llrawi~lg~ ;
Fig.1 is an assembl:Lng explanatory view ol the bearing in a Plrst embodimellt of thls inventioll.
Fly.2 ~s a sectional explanatory view along the line II- II
of Fig.1.
Fig.3 is an explanatory view of a guide pin in the first embodiment.
Fig.4 is an assembling explanatory v:le~v ill a second embodiment of this invelltion.
Fig.5 i5 an assembling explanatory view in a third embodlmerl t o~ thi s i nvention.
Fig.6 is an assembling e~planatory view in a fourth embodiment of this invention.
Detailed description of the Preferred Embodiment ;
[Example 1]
In Fig.1 to Fig.3, the bearing A comprises an inner ring 1 to be engaged with the axis, an outer ring 2 to be attached to a machine frame or a casing and a plurality of gu:lde pins 3 fi-t to the outer ring 2.
The inner ring 1 is formed by press~formlng an oxide ceramics material of a material such as PSZ (partially stabilized Zirconia) or alumina, etc. by filling it in a mold and then sintering a molded product at 1500C to 1600CC. An axial hole 4 for engaging the axis is formed at the center of the inner ring 1. The axial hole is formed so a~ to have a fixed engaging allowance according to a diameter of the axis to be engaged with the axial hole 4.
2026'1~
I'he numeral 6 is all axial cetlter of the axial hole and corresponds to the a~ial cen-ter of the bearlng ~.
~ ~lldiny surface la i5 formed on -the outer periphery of the inner ring 1 in parallel to the axial center 5. The sliding surface la transmits a radial load applied on the axis to the outer ring 2 by the sliding contact with the sliding surfacs 2a formed at the outer ring 2 described hereinaft~r. For this purpose, the sliding surface la i5 necessary to be parallel to the axial center 5 correctly.
ht -the approximately middle portion oE the sliding surfa~e la formed on the outer periphery of the lnner ring 1, a ring shape groove b is formed all around -the inner ring 1. The groove 6 constrains the moving direction of the lnner ring 1 only in a rotational direction by latching with guide pin 3.
~ he outer ring 2 i9 also formed by press-forming filling an oxide ceramics material such as PSZ or alumina etc. in a mold as same as in tlle illner ring 1 and then sinterillg it at 1500 C
to 1600 C.
At the inner of the outer ring 2, a sliding surface 2a formed so as to have a fixed allowallce with respect to the sliding surface la formed on the outer periphery of the inner ring 1 is formed. The sliding surface 2a is formed so as to have an approximately equivalent length to the sliding ~urface la of the inner ring and contacts with the sliding surface la slidably whereby a radial load applied on the axis is transmitted through the inner ring 1. For this purpose, the sliding surface 2a is construc-ted by a parallel surface to the ~2~18~
axial centet~ 5.
~ p].urality of holes 7 for erl~clylt~g g-licle pins 3 are formed at approximately midclle portion in the axial direc-tion of the outer riny 2 and positions corresportcl:itlg to the groove 6 formed a~ the inner ring 1. The sllape of the hole 7 is that of the guide pin 3, namely a circular sha]?e or a polygon ancl the dimension thereof is formed to be approxlmately equivalent to that of the gulde pin 3.
The outer periphery 2b of the outer ring 2 ls formed to be cylindrical sllap~ parallel to the axi~l center 5. The both end surfaces ~c of tlle o~-ter ring 2 i5 con~trllcted as a rectangular plane against the axial center 5. The outer periphery 2b arld the end surface 2c become engaged por-tions when they are a-ttached to a machine frame or a Ca.SinCJ not illustrats the b.earing A.
The guide pin 3 i5 formed by press-forming an oxide ceramics material sucll as PSZ and alumina etc. filling it in a mold and sintering a molded produc-t thereof at approximately 1500~C to 1600 C.
The guide pin 3 may be so called a straight pin or a taper pin. Further, a shape of guide pin 3 (3a to 3c) may be a cylindrical pin 3a as ~hown in Fig,3(A) or may be a square pin 3b as SIIOWII itl Fig.3(B). Further, a pin 3c having a flange at the end portion as shown in Fig.3(C) may be usecl. In -this embodiment, the cylindrical pin 3a is used as guide pin 3.
The guide pin 3 i5 formed to be equal to -the wide dimension of the groove to formed at the inner ring 1 or to _ ~ _ 202~.85 some~ al- small dlm~ ion thereof. ~ccordlllgly, th~re i~ no an~ciety of occurrence o~ play hetween the gu:lcle pin3 and groove 6.
Further, number of guide pin 3 i5 desirable -to be 3 or more than 3. This is due tc the fact when number of guide pin is few and a load in a thrust direction applies on the axls of the inner ring 1, there i5 anxiety that a bellding stress applie~
to the guide pin 3 due to said load.
I'he axial hole 4, the sliding surface la, tlle groove 4 in the inner ring 1 and the sliding surface 2a, the outer periphery 2b, the end surface 2a and the hole 7 etc. in the outer xlng 2a are formed simultaneously when the inner and outer rings are press-formed.
In t~le above press forming, the dimensiorl accuracies of the inner ring 1 and the outer r-ing 2 are possible to obtain approximately~ 0.005mm in accuracy against designed dimension of each part. Further, surface roughness can be secured about R~ O.B.
In order to construct the bearing A using the inner ring 1, outer ring 2 and guide pin 3 constructed as shown in the above, the sliding surface 2a i5 allowed -to contact wit~ the sliding surface la slidably by engaglng the inner ring 1 with the outer ring 2. The groove 6 formed at the inner ring 1 is opposed to the hole 7 formed at the outer ring 2 and the guide pin 3 is inserted in-to each hole 7, top end of said guide pin 3 being allowed to latch with groove 6.
~t this time, the guide pin 3 can be adapted to fix to 202618~
t}le oute~ rilly 2 by applyillg an adlle3ive to tlle~ corresponding part ~Jit~ t}le hole 7 of thc! gu:L~e pin 3 ancl engaying said pin 3 witll llole ~. E'urtll~r, -tlle guide pill 3 can be adapted to fix to the outer ring 2 by exparlding the llole 7 hea-t:lrlg -the outer ring 2 and ellgagillg the guide pin 3 in normal temperature sta-te to the llole 7, so called thermal :insert. Furl.hermc)re, the gulde pin 3 can be adapted -to fix to the outer riny 2 by cooling the guide pin 3 to shrink by means of col~ agent such a'3 liqulde nitrogen etc. and engayillg saicl pin 3 -to the outer rillg 2 in normal state, so called coollng insert.
It is de~sirable to perform a grinding proces3ing to the sliding surface la, the groove ~ of -the inner ring 1, and the sliding surface 2a and the pin 3 of t~le outer ring 2 separately which cons-titutes the bearing A accvrdirlg to the accuracy requested for said bearing A.
Further, the lapping of the contact surface of the sliding surface 2a with the sliding surface ta, the yuide pin 3 and the groove 6 are also possible after engaging the inner ring 1 -to the outer ring 2. The lapping can be practi~ed by giving an abrasive agent such as diamond powders, etc. to each contact surface and a relative rotation tllereto.
The rotation of the bearing A becomes to be smootll by grinding the inner and outer rings and guide pin 3 and groove 6 respec-tively or lapping them.
In the bearing A constructed as described above, the top end portion of the guide pin 3 fixed to the outer ring 2 is inserted into the groove G formed at the inner ring 1. By this, g 202~18~
tlle outer ring 2 by applyin~ an adhesive to the corresponding part ~ith -t}le hole 7 of the gu:ide pin 3 and engaging said pin 3 witll ho1e 7. Further, the guide pin 3 can be adapted to fix -to the outer ring 2 by exparldiny the hole 7 heat:ing the outer ring 2 and engagillg the guide pin 3 in normal tempera-ture state to the holc ~, so called thermal insert. Furl:hermc)re, -the guide pin 3 can be adapted to fix to tlle outer ring 2 by cooling the guide pin 3 -to shrillk by means of cold agent StlCh as liquide nitroyen etc. and engagillg said pin 3 to the outer ring 2 in normal sta-te, so called cooling insert.
T t is desirable to perform a grinding processing to the sliding surface la, the groove 6 of the inner rlng 1, and the sliding surface 2a and the pin 3 of the outer ring 2 separately which cons-titutes the bearing A accvrdiny to the accuracy requested for said bearing A.
Further, the lapping of the contact surface of the sliding surface 2a with the sliding surface la, the yuide pin 3 and the groove 6 are also possible after engaging the lnner ring .t -to the outer ring 2. The lapping can be practised by giving an abra~i-ve agen-t such as diamond powders, etc. to each con-tact surface and a rel~tive rotation theretor The rotation o~ the beariny ~ becomes to be smooth by grinding the inner and outer rings and guide pin 3 and groove 6 respectively or lapping them.
In the bearing A constructed as described above, the top end po.rtion of the guide pin 3 fixed to the outer ring 2 is inserted into the groove 6 formed at the inner ring 1. By thi~, g 2(~26~l8~i 12a corre~polld~ to t~le slldiny ~ t~ ce lla 13 ~orme-l and a plane 12c which is appro~lmately r:lyllt angle W:ltll the axial aenter 15 i9 formed connecting wi~ the sllditly surfaoe 12a. ~-t a ridged line formed by the sl.idincJ surface 12a and tlle plane 12c, a very small ~aper surface formed at a taper angle equivalent to the -taper surface llb O:e the inner ring 11 is constructed, said taper surface being constrllcted as the slidillg member 12b. The slidin~ portion 12b contacts slidably with -the taper surface llb formed at the intler ritly 11 and suppo;tts a load in -the thrust direction applied on the axis engacJed wi-th tle inrler rin(3 11.
Further, the end surface 12d at the fron-t elld side of the outer riny 12 is const:ructed as a rig}lt angle surface with the axial center 15.
A-t the latchiny member 13, is formed a hole 13 at the center having a laryer diameter thatl that of the axial hole 14 formed at the inner ring 11. Further, the outer diameter of the latching member 13 is formed to be larger than that of the sliding surface lla of the inner riny 11 and smaller than that of the outer diameter of the ou-ter ring 12. Furthermore, at one surface of the latching member 13, is formed a ring shape projection 13b engaged with the groove 16 formed at the inner ring 11.
In order to construct the bearing B by the inner ring 11, the outer ring 12 and the latching member 13 constructed as above, the inner ring 11 is engaged wi-th the outer ring 12 to allow to contact tlle sliding surfaces 12a, lla and the taper -surface llb with -the sliding portion 12b slidably, and then the 2~2~18~
oJecl::loll 13b o~ tlle l.al clllng member 13 i:3 allowed to enyage w:Lth the groove 16 formed at the :Inner r:lng 11. ~fter that, the latching member 13 i3 fixed to -the i/lner rillg 11 by mean3 of applying all adhesive agent, thermal insertlon, or cooling insertioll to the projection 13b.
In -the bearing B thus constructed as described above, the sliding surface lla formed at the inner ring contacts ~lidably with the sliding surPace 12a formed at the outer ring 12 thereby being able to suppor-t the load in the radial directioll applied to the axis enyayed with the inrler ring 11, Further, the taper surface 11b formed at the inner ring 11 contacts slidably with the slidiny portion 12b formed at the outer ring 12 thereby being able to support the load in the thrust direction applied to the axis.
Thus in the bearirlg B, the taper surface llb of the inner ring 11 contacts slidably witll the sliding portion 12b of the outer ring 12 thereby preventing the transference of the inner ring 11 in a direction shown by the arrow, Since the latching member 13 fixed to the end surface llc of the ~nner ring 11 has a larger diameter than that of the sliding surface 11a, the transference of the inner ring 11 in b direction showll by the arrow can be prevented.
In Fig.5, the bearing C is constructed by the inner ring 21, the outer ring 22 and the latching member 23. The inner ring 21, the outer ring 22 and the latching member 23 are formed by forming the ceramic3 ma-terial and sintering as same as in each embodiment described above.
~02618~
Al ~ e cent~r of l:lle inller r:ing 2l, tlle a~sial hole 24 for engag~ the axls rlot il:Lustrate(l is formecl correspondirlg to the axia]. cellter 25 of the bear:Lng C.
'l'he outer ~haE)e of the :inller ring 21 is lormed to be a curved surface shape, said curved sur~ace heing constructed as a sliding surface 21a, ~-t the front side of tlle lnller riny 21 a cylindrical bos~ portion 2lb is formecl connectillg with the sliding sur~ace 21a, at the end sur~ace 21c of said boss portion 2lb being formed a ring shape groove 26 so tllat the center thereof may be corresporlded to the axlal cer-ter 25.
The inner peripllery of the outer riny 22 is formed with a shape corresponds to the shape of the sliding sur~ace 21a formed at the inller ring 21, said inner periphery .sur~ace being constructed as a sliding surface 22a. F'urther, a hole 22b is formed continuillg Witil the sliding surface 22a. The hole 22b ls formed so as to have a comparstively larger dimension than that of the outer dlameter of tlle boss port iOII 2lb ~:ormed at the inner r:ing 21.
The latching member 23 is rormed with appro7~imately same shape with said latching member 13. Namely, at the latching member 23, a hole 32a i~ provided with a larger dimension than that of a diameter of the axial hole 24 formed at the inner ring 21 corresponding to the a~.ial center 25 o~ the bearing C.
Further,formed is a projection 23b having a center corresponds to t}le ax:ial cerrter 25.
In order to constitute the bearing C by -the inner ring 21, outer ring 22 and latching member 23 constructed as 2~2~
de.scribed above tlle J.nller rilly 21 :i~ enyacJed w.Lth the outer rirlg 22 -the slicllng sur~ce 21a :i5 allowed to contact slidably wlth the sliding surface 22a and tllen the E~rojection 23b of the la-tchiny member 23 is allowed to enyage ~ith groove Z6 formed at the end surface 21c of the inllel r.ing 21. The latching member 23 is Lixe~ to -the inner ring 21 by mean~ of apply:ing an adhesive agent to the proje~tion 23 or thermal or cooliny inser-tion etc.
In the bearing C thus constructed even when the load in radial directioll and tll~ load in ~llrust direction applied simultaneously to the axis erlyaged with inner ring 21 by the sliding contact o~ the sliding surface 21a ~vith tlle sliding surface 22a said axis can be supported smoothly. Since the sliding surfaces 21a and 22a of the bearing C are formed to be a curved surface shape the bearing C possesses an automatic adjustment function.
The bearing C is possible to prevent the trnsfer of the inner ring 21 in c direction shown by tlle arrow by the contact of sliding surfaces 21a 22a and further to prevent its trnsfer in d direction sho~n by tlle arrow.
In Fiy. 6, the axis D is constructed by a cap-like latching member 33. Said inner ring 31 tlle outer ring 32 and the latching member 33 are formed by forming ceramics material and sintering it as same as in each embodiment described above.
At the center of the inner ring 31 an axial hole 34 for engaging an axis not illustrated therein is formed corresponding to the axial center 35 of the bearillg D. At the vuter periphery 202~
o~ tlle ~ ler rilly 31, a .sLldlllg suL~face 31a pclrallel 1:o the a~ial cerlter 35 i5 fOr~ne(l, 9aid sl:idlll(J surface 31a forming a -taper surface 31 conllectillcJ therewith at -the frollt slde of the inrler r:LIlg 31. Further, the cyl:illdrical sur~ace 31c is formed continuillg with said taper surface 31b.
~ t tlle inner periphe:ry of the outer riny 32, is formed the sliding surface 32a which contacts slidably with the sliding suriace 31a formed at the lnrler xlrlg 3l. ~t the ~ron~ side of the sliding surface 32a, the surface 32c approximately rectangular to the axial cerlter 35 and a cyl:lndrical surface 32d havillg a smaller diamete~ thall l:llat oL the slidlng surface 32a parallel to the axial center 35 are formed. The surface 32cl is formed with a compactively larger dimension than that of the outer diameter of the cylindrical surface 31c formecl at the inller ring 31. ~o the ridged lille constructed by the surfaces 32c and 32d is provided a sliding portion 3Zb which supports the load in -tlle thrust direction applied to the inner ring by abutting the taper surface 31b formed at -the inner riny 31 as same as in the secolld embodiment.
At the surface 32e of the rear side of the outer ring 32, a step por-tion 36a continued to the outer periphery 32f of the outer ring 32 is formed. The step portion 36a is formed to be a ring shape corresponds to the axial center 35 as its center.
The latching member 33 is formed so that the outer diameter may be approximately equivalent to the outer diameter of the outer ring 32 or a somewhat smaller diameter, and a ring shape project ion 33b havillg a cen-ter eorrespondillg to the axial 20261~
cellterl 35 is formed. 'rhe heigllt o~ the projection 33b is formed so as to ~e appro}cimately equ:lvalent -to the dep-th of the s-tep 36a. FUI~ ther, the numeral 33a is a hole formed to be a larger diameter than that of the axial hole 3~.
In order to cons-truct the bearing D by the inner and outer rings 31 and 32 respectively and the latching member 33, after engagillg tlle inner riny with tlle outer ring 32, the latching member 33 is fi~ced to the outer ring 32 by applying the adhesive ayent to the outer ring 32 or thermal insertion or cooling insertloll of -the outer ring 32 as same as ln the embodiment describe above.
In the above bearlng D, slnce -the outer per.iphery of the latching member 33 does not projec-t more than outer ring 32, an attaching working of the bearing D to the machine frame, etc.
can be performed smoothly using the outer periphery 32f of the outer ring 32 as a guide. Further, by sliding contact of the sliding surface 31a witll the sliding surface 32a, the load in the radial direction applied to the axis engaged with the lnner ring 31 is supported and by the sliding contact of the taper surface 31b with the slidiny port.ion 32b, the load in the thrust direction can be supported.
The above bearing D prevellts the transfer of the inner ring 31 in e direction shown by the arrow by the abutmen-t of the taper surface 31b against the sliding portlon 32b and prevents the transfer of the inner ring 31 in f direction shown by the arrow by the latching member fixed -to the outer ring 32.
As described above, by forminy a step portion 36a having 202~18~
a same funct.Lo~l a~ tlle ~3roove lll eacll above embodimerlt at the conrlect~ y portion of the outel peril)hery 32f allc1 the rear end e.llrface 32e of the outer r-lng 32 the form of the outer ring 32 become easy.
In each above bearing ~ to ~ since the inrler and outer rings are made by ceramics respec-tively tlle fric-tion coefficient becomes smal] thereby decreasing the frlction loss thereof. By this there is no need of tlle lubrication agains-t the sliding surface. Further even when the heat is generated due to tlle sllding there occurs no exc:eQ.s of the -thermal stre~s due to tlle thermal exparlsion of the iIIner and outer ring~
because tlle coefficietlt o~ the thermal expansion is about 8 to 11XlO 6/~C. Further since the heat temperature resistance of the ceramics is about 600'G to lOOO~C there is no fear of deterioration of the inner arld outer rings due to the heat yenerat ion .
Claims (5)
1. In a ceramic bearing constructed by contacting a ceramic outer ring slidably with a ceramic inner ring, said ceramic bearing is characterized by being provided with a latching member so as to prevent a transfer of the ceramic outer ring or the ceramic inner ring in an axial direction of the ceramic inner ring.
2. A ceramic bearing according to claim 1 wherein said latching member is a pin made of ceramics.
3. A ceramic bearing according to claim 1 wherein said latching member is formed to be a circular plate shape.
4. A ceramic bearing according to claim 3 wherein a hole for loosely inserting an axis is provided at a center of the latching member formed like a circular shape.
5. A ceramic bearing according to claim 3 or 4 wherein a projection engaged with the inner or outer ring is formed at the latching member formed to be a circular shape.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1-263909 | 1989-10-12 | ||
| JP1263909A JPH03129119A (en) | 1989-10-12 | 1989-10-12 | Ceramic bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2026185A1 true CA2026185A1 (en) | 1991-04-13 |
Family
ID=17395952
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002026185A Abandoned CA2026185A1 (en) | 1989-10-12 | 1990-09-25 | Ceramic bearing |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US5127745A (en) |
| EP (1) | EP0422786B1 (en) |
| JP (1) | JPH03129119A (en) |
| KR (1) | KR950008332B1 (en) |
| AT (1) | ATE119249T1 (en) |
| CA (1) | CA2026185A1 (en) |
| DE (1) | DE69017342D1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE9204349U1 (en) * | 1992-03-31 | 1992-11-12 | Feodor Burgmann Dichtungswerke Gmbh & Co, 8190 Wolfratshausen, De | |
| CN1145107A (en) * | 1994-02-08 | 1997-03-12 | 塑料轴承及外罩澳大利亚西亚有限公司 | Plain bearing |
| US5556499A (en) * | 1994-12-01 | 1996-09-17 | Polaroid Corporation | Delaminating method and apparatus |
| JPH11267966A (en) * | 1998-03-24 | 1999-10-05 | Speedfam Co Ltd | Duplex polishing machine |
| US6505974B2 (en) | 2001-05-02 | 2003-01-14 | Honeywell International, Inc. | Ceramic ball bearings and assembly |
| US6746153B2 (en) * | 2001-09-25 | 2004-06-08 | The Anspach Effort, Inc. | Bearings for surgical instruments |
| US7080973B2 (en) * | 2003-11-18 | 2006-07-25 | Hon Hai Precision Industry Co., Ltd. | Fan seat and method for producing it |
| US20060051004A1 (en) * | 2004-09-09 | 2006-03-09 | Lee Yu H | Ceramic bearing assembly |
| US7320549B2 (en) * | 2005-05-16 | 2008-01-22 | Sankyo Dilless Industry, (Usa) Corp. | Self-lubricating bushings, bearings and bearing assemblies |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE732724C (en) * | 1936-08-15 | 1943-03-10 | Ellinger & Geissler | Arrangement to secure against axial displacement of shafts with changeable electrical switching elements |
| GB567905A (en) * | 1943-09-02 | 1945-03-07 | Owen David Lucas | Improvements in bearings |
| CH281535A (en) * | 1950-01-07 | 1952-03-15 | Keller Friedrich | Ring plain bearings. |
| GB704035A (en) * | 1951-10-25 | 1954-02-17 | Murex Ltd | Bearings and the like |
| US3071419A (en) * | 1960-05-13 | 1963-01-01 | Dodge Mfg Corp | Bearing or the like |
| US3578828A (en) * | 1969-02-18 | 1971-05-18 | Kaman Aerospace Corp | Split-race bearing construction |
| US3726572A (en) * | 1969-05-14 | 1973-04-10 | Smiths Industries Ltd | Gas-lubricated bearings |
| GB1437532A (en) * | 1973-06-29 | 1976-05-26 | Sealed Motor Const Co Ltd | Pump units |
| US4477197A (en) * | 1981-04-21 | 1984-10-16 | Sargent Industries, Inc. | Bearing |
| JPS60205011A (en) * | 1984-03-28 | 1985-10-16 | Hitachi Ltd | Self-lubricating bearing |
| EP0258845A3 (en) * | 1986-08-29 | 1988-08-17 | Kabushiki Kaisha Nagano Keiki Seisakusho | Ceramics bearing |
| JPH0193620A (en) * | 1987-10-01 | 1989-04-12 | Toshiba Tungaloy Co Ltd | Bearing device for electronic equipment |
-
1989
- 1989-10-12 JP JP1263909A patent/JPH03129119A/en active Pending
-
1990
- 1990-08-21 KR KR1019900012889A patent/KR950008332B1/en not_active IP Right Cessation
- 1990-09-20 DE DE69017342T patent/DE69017342D1/en not_active Expired - Lifetime
- 1990-09-20 EP EP90310285A patent/EP0422786B1/en not_active Expired - Lifetime
- 1990-09-20 AT AT90310285T patent/ATE119249T1/en not_active IP Right Cessation
- 1990-09-25 CA CA002026185A patent/CA2026185A1/en not_active Abandoned
- 1990-10-05 US US07/593,797 patent/US5127745A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| EP0422786A2 (en) | 1991-04-17 |
| EP0422786B1 (en) | 1995-03-01 |
| EP0422786A3 (en) | 1991-09-11 |
| DE69017342D1 (en) | 1995-04-06 |
| JPH03129119A (en) | 1991-06-03 |
| KR950008332B1 (en) | 1995-07-27 |
| KR910008298A (en) | 1991-05-31 |
| ATE119249T1 (en) | 1995-03-15 |
| US5127745A (en) | 1992-07-07 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |